Gyratory crusher



March 28, 1961 E. H. Bx-:YHL 2,977,057

GYRATORY CRUSHER Filed May 16, 1958 3 Sheets-Sheet 1 15o Jaz l i 136 i v v l 154 5&6 f "3@ 126 la f g llltzili 14:8

'I m t ATTORNEYS.

MalCh 28 1961 E. H. BEYHL 2,977,057

GYRATORY CRUSHER Filed May 16, 1958 5 Sheets-Sheet 2 wi 'f/ //7% 16; -Elam Z INVENTOR: 1(56 Ewvd H-B/eyhl,

ATTORNEYS.

March 28, 1961 E. H. Bl-:YHL

GYRATORY CRUSHER 3 Sheets-Sheet I5 Filed May 16, 1958 INVENTORI V Edwvpd I-.LB/qyhl ATTORNEYS.

GYRATORY CRUSHER Edward H. Beyhl, Allentown, Pa., assigner, by mesne assignments, to Fuller Company, Catasauqua, Pa., a corporation of Delaware Filed May 16, 1958, Ser. No. 735,757

7 Claims. (Cl. 241-213) @This invention relates to gyratory crushers of the type having an upright shaft to which a gyratory movement is imparted by a rotary eccentric and on the upper end of which shaft is secured a crushing head opposed to a concave. In the type of crusher with which this invention is concerned the shaft is supported for vertical adjustment to vary the position of the head relative to the concave in order to adjust the machine for a fine or a coarse output of crushed material.

Although there are many known types of adjustable supports for the shaft of a crusher of the type with which this invention is concerned, it is an object of this invention to provide an improved and simplified adjustable support for the shaft of a gyratory crusher. It is a further object of this invention to provide such a support that may be adjusted, to vary the fineness of the crushed output, while the Crusher is in operation.

In Crushers of the type with which this invention is concerned the concave usually is secured to a support or retainer that has -a circumferential flange overlying a corresponding flange on the rim of the crusher frame. The concave retainer usually is secured to the machine frame by elongated bolts or tension rods that extend through the retainer and rim flanges. Springs usually `are interposed, however, between the undersurface of the rim flange and lower abutment rings, through which the bolts extend, in order to yieldably secure the retainer in place. Thus, the concave can yield upward or tilt, under undue crushing stresses, in order to prevent damage to the crusher. In machines of this type, however, the springs ordinarily must be removed in order to remove the concave for purposes of repair or replacement, or in order to repair or replace the Crusher head. Consequently, in replacing the concave or pressure head the springs must be reassembled and also readjusted to their proper degree of compression.

It is, therefore, another object of this invention to provide a construction wherein the movement-resisting springs for the concave need not be removed on removal of the concave retainer and wherein the spring adjustment may be maintained irrespective of removal and replacement of the concave and/or the crusher head.

Additionally, in Crushers of the type under consideration, the concave usually is secured to the concave retainer by a complicated mechanical arrangement or by an arrangement wherein molten metal is poured into a recess between the two parts to secure them together. It is, therefore, another object of this invention to provide a simplified mechanical construction for securing a concave to a concave retainer, and wherein the frustoconical engaging surfaces of the concave and its retainer may be'machined with facility, for centering purposes, before the parts are assembled.

Other objects and advantages of the invention will become apparent from the following description and the accompanying drawings in which:

Figure 1 is a vertical sectional viewv of a gyratory crusher embodying this invention.

Patented Mar. 23, i961 `fFigure 2 is a plan view with parts broken away of the Crusher shown in Figure l. Y

Figure 3 is a sectional view taken substantially on line 3-3 of Figure l.

Figure 4 is an enlarged view of the undersurface of a bearing member on the lower end of the shaft of the crusher shown in Figure 1. l

Figure 5 is an enlarged plan view of a bearing member on the upper end of the adjustable step bearing sho-wn in Figure l.

Figure 6 is an enlarged fragmentary sectional View taken substantially on line 6--6 of Figure l.

Referring now to the drawings, the crusher includes a frame 10 having a central upstanding hub portion 12 provided on its interior with a bushing 14 in which is journalled an eccentric 16V. The lower end of the eccentric 16 is supported on a washer-like annular thrust bearing 18 which, in turn, is supported on a 'dat annular ledge 20 formed by the upper end of a tubular lower extension 22 attached by screws 24 to the hub portion 12. The lower end of the hub portion 12 is interiorly enlarged for the reception of a bevel gear 26 keyed to the lower end of the eccentric 16 and meshing with a pinion 28 on the inner end of a lateral driving shaft 90. The driving shaft 30 preferably is mounted in anti-friction bearings 32 in a lateral hub portion 3-4 of the frame lil and has a drive pulley 36 on its projecting outer end.

The eccentric 16 has an eccentric bore 38 the axis of which is tilted relative to Ithe axis of rotation of the eccentric. Rotatably mounted in the eccentric. bore 3S, through the intermediary of a bushing 40, is a cylindrical portion 42 of an upstanding shaft 44 which can be moved axially relative to the eccentric 16 and to which rotation of the latter imparts gyratory movement. Mounted on an upwardly tapering portion 46 of the shaft 44 above the cylindrical portion 42 is a crushing head y48 comprising a core 50 and a ymantle 52 which constitutes a gyrating crushing jaw opposed to a xed jaw constituted by a concave'54 secured within a ring-like concave retainer 56. At its upper end the retainer 56 is provided with an outwardly extending flange 58 having a circular channel 6i) in its undersurface which fits over a corresponding upstanding rib 62 on the upper surface of a circumferential flange 64 on 'the upper rim of the frame 10.

The lower end of the tubular extension 22 is closed by a cap 66, which may be secured to the extension by bolts 68.' Disposed within the tubular extension 22 and cap 66 for receiving the downward thrust of the shaft 44 is an upstanding stub shaft or step bearing 70 having an upper cylindrical portion 72 journalled within the extension through the intermediary of longitudinally-spaced bushings 74, an intermediate portion provided with a coarse thread 76 of low pitch, and a lower cylindrical portion 78 journalled in the cap 66 through the intermediary of a bushing 80. Keyed within the tubular extension 22 is a sleeve 82 having an interior thread engaged with the bearing thread 76 and a downwardly facing exterior shoulder -tseated on a complementary shoulder 85 in the extension. Consequently, rotation of the hearing 70 adjusts the same vertically. it will be noted that the threads 76 are of low pitch, large and long to withstand the high downward thrust of the shaft e4.

In order -to rotate the bearing '70 a worm gear 8S is splined onto the lower cylindrical portion 7S thereof, as by keys 9i) on the gear disposed in longitudinal key-ways in the bearing extending the entire length of the lower portion thereof, The worm gear 88 is seated on a flange 92 at the upper end of the bushing S9 which constitutes a thrust bearing for the gear. r`A worm 94 (Figure 3) meshing with the worm gear S-S is journalled ina lateral enlargement of the tubular extension 22 and cap 66, andv extends to the exterior thereof where it may be provided with an appropriate driving gear 96 that may be driven by any suitable motor (not shown),` such as an electric motor. Of course, the worm 94 may be driven manually, as by a hand crank (not shown) instead of by a motor. It is to be noted that the engagement between the worm gear 88 and the worm 94 is such as to be substantially self-locking against reverse movement, i.e., movement of the worm by the gear.

The lower end of the shaft 44 is supported on the upper end of the step bearing 70 through the intermediaries of a bronze planar thrust bearing 98 supported on the upper end of the step bearing, a planar-concavo steel thrust bearing 100 seated on the bearing 98, and a bronze thrust bearing 102 having a convex spheroidal surface 104 engaged with the concave side of the steel thrust bearing 100. Preferably, the planar bearing 98 is retained against lateral movement on top of the step bearing 70 by dowel pins 106 recessed below the upper surface of the planar bearing, while the thrust bearing 102 is retained on the lower end of the shaft 44 by a central screw 108.

Preferably, all three of the bearings 98, 100 and 102 are centrally apertured and the convex surface of the bearing' 102 and both surfaces of the planar bearing 98 are provided with grooves 110 and 112, respectively, which radiate outwardly from the central apertures to the periphery of the respective bearing, as shown in Figures 4 and 5. Lubricant is supplied to the central apertures of the bearings 98 and 102 for flow outwardly through the grooves 112 and 110, respectively, therein through an oil inlet passageway 114 in the side of the tubular frame extension 22. The passageway 114 terminates at its inner end at a location between the two bushings 74, the space between the latter constituting, in effect, a circumferential groove 116. The cylindrical portion 72 of the step bear ing 70 is provided with a longitudinal groove 118 adapted to overlap the groove 116 in all positions of axial or vertical adjustment of the bearing. An oil passageway 120 extends through the bearing 70 from the bottom of the groove 118 to a central location in the upper end of the step bearing in registry with the aperture in the thrust bearing 98.

It will be seen that oil supplied under pressure, in any appropriate manner, to the oil inlet 114 will thoroughly lubricate the thrust bearings 18, 98, 100 and 102, the gears 26 and 28, the bushings 14, 40, 74 and 80, the threads 76, the worm gear 88, and the worm 94. A separate oil inlet 115 in the lateral hub portion 34 preferably is employed to supply oil to the bearings 32. Preferably, an oil outlet 122 is provided in the frame 10 adjacent the lower portion of the inner end of the lateral hub portion 34. It will be noted that the provision of oil grooves 112 on both sides of the planar bearing 98 both prevents incorrect assembly thereof and increases cooling of the parts by oil owing in the grooves opposed to the top end of the step bearing 70.

Bolted to the frame flange 64 is the outer rim 124 of a spider 126 having a central bushed hub portion 128 within which is journalled the upper end of the gyratory shaft 44, the upper end of the hub portion 128 being closed by a detachable cap 130. A feed hopper 132, having longitudinal slots 134 in its lower end to accommodate the arms 136 of the spider 126, is mounted on the spider arms 136, as by outer eyelet lugs 138 on the hopper resting upon and bolted to corresponding lugs 140 on the spider arms.

In order to relieve undue stresses on the machine which might occasion breakage thereof, as by the passage of tramp metal between the concave S4 and the crushing head 48, the concave retainer 56 is mounted so that it can tilt or move upwardly relative to the frame on the exertion on the concave of an undue upward force. 'For this purpose, bolts 142 extend downwardly through aligned apertures in the ange 58 of the retainer 56 and the flange 64 of the frame `1l). A segmental abutment ring 144 is secured on the lower ends of the bolts 142, as by nuts 146, in opposition to the undersurface of the frame flange 64, and a corresponding segmental abutment ring 148 is mounted on the bolts 142 in underlying engagement with the aforementioned undersurface. Springs 150 interposed between the two abutment rings 144 and 148 constantly retain the concave 54 in proper operating position but will yield under undue force to permit the retainer 56 and concave 54 to raise or tilt to avoid damaging stresses to the machine.

The spring force can be adjusted by adjusting the nuts 146, and since the assembling of the springs 150 and adjustment of their degree of compression between the abutment rings 144 and 148 is a both difficult and timeconsuming task, it is desirable to provide a construction wherein the springs and their abutment rings need not be disassembled from the machine when the retainer 56 is removed for replacement or repair of the concave 54. It also will be seen that the retainer 56 must be removed to permit repair or replacement of the crusher head 48 and/or the shaft 44.

Accordingly, a plurality of shorter bolts 152 extend downwardly through the flange 64 on the frame 10 and have their heads recessed into counterbores 154 in the rib 62. The lower ends of these bolts 152 extend through aligned apertures in both of the abutment rings 144 and 148 and have nuts 156 secured on their lower ends to bear against the underside of the lower ring 144. Consequently, adjustment of these nuts 156, simultaneously with the adjustment of the nuts 146 on the longer bolts 142, will serve to maintain the springs 150 and their abutment rings 144 and 148 in an assembled con dition with a set predetermined degree of compression even though the longer bolts 142 are removed to permit removal of the concave retainer 56.

The inner surface 158 of the retainer 56 is of frustoconical -configuration for mating engagement with the corresponding exterior surface 160' of the concave 54. These two surfaces 158 and 160 normally are machined accurately so that the concave 54 will be properly positioned and centered with respect to the gyratory axis of the shaft 44. In order to support the concave 54 on the retainer 56 the interior surface 158 of the latter is provided, adjacent its upper end, with a pair of diametrically opposed recesses 160, each generally T-shaped in configuration with the leg portion 162 of the T extending longitudinally downwardly, as best shown in Figure 6. Thecross or transverse portion 164 of each recess 160 is provided, on opposite sides of the leg portion 162, with planar wall surfaces 166 facing the apex or smalle'i end of the inner surface 158 of the retainer 56. As is best shown in Figure 6, these surfaces 166 preferably are inclined upwardly away from the opposite sides of the leg portion 162 of the recess 160.

The outer surface 160 of the concave 54 is provided with a pair of diametric lugs 168 corresponding to the retainer recesses 160. These lugs 168 are of such Width that they Will pass freely upwardly through the leg portions 162 of the recesses 160 during assembly of the concave 54 in the retainer 56, so that the concave can be moved first axially into the retainer, and then turned slightly to engage the lugs 168 against the inclined wall surfaces 166 of the recesses, to therebyloek the concave to the retainer, Preferably, each lug 168 is provided with oppositely inclined planar surfaces 170 for mating and wedging engagement with one or the other of the recess surfaces 166. The direction of turning of the concave 54 to lock it to the retainer 56 will depend upon the direction of rotation or gyrationof the shaft 44, and the lugs 168 are engaged with one or the other of the recess wall surfaces 166 so that the engagement therebetween will be tightened by operation of the crusher. The lugs 168 preferably are welded to the concave 54 after the outer surface 160 of the latter has been machilled, in order 'to facilitate such machining.

It thus will be seen that the objects of this invention have been fully and effectively accomplished. It will be realized, however, that the foregoing specific embodiment has been shown and described only for the purpose of illustrating the principles of this invention and is subject to extensive change without departure from such principles. Therefore, this invention includes all modifications encompassed within the spirit and scope of the following claims.

I claim:

1. In a gyratory crusher having a frame, an upstanding gyratory shaft carried by the frame, a crushing head on the shaft, and a concave carried by the frame in opposition to the head, the combination comprising: a step bearing supporting the lower end of the shaft and threadedly engaged with the frame for effecting vertical adjustment of said bearing by rotation thereof relative to the frame, vertical adjustment of said bearing effecting like adjustment of theA shaft and head to vary the size of the product of the crusher; and a bearing-rotating mem` ber rotatably mounted on the frame and engaged with said bearing for rotating the latter, said bearing-rotating member also being engaged with said bearing to permit relative axial movement therebetween, whereby rotation of said member effects vertical adjustment of the shaft and the step bearing transmits the downward thrust of the shaft to the frame independently of said bearingrotating member.

2. The structure defined in claim 1 in which the member comprises a worm gear splined to the bearing and including a worm engaged with said gear.

3. The structure defined in claim 1 in which the bearing includes upper and lower cylindrical portions having rotary bearing engagement with the frame and an intermediate threaded portion.

4. The structure defined in claim 1 including means defining upwardly-concave spheroidal thrust bearing surlfaces between the step bearing and the shaft lower end,

vsupply passageway in the step bearing communicating with the opening.

6. In a gyratory crusher having a frame, an upstanding gyratory shaft carried by the frame, a crushing head on the shaft, and a concave carried by the frame in opposition to the head,lthe combination comprising: a tubular frame portion below the shaft having a closed lower end; la step bearing threadedly engaged within said portion gand supporting the lower end of the shaft, rotation of said bearing effecting vertical adjustment thereof with like adjustment of the shaft and head to vary the size of the product of the crusher; a gear splined on said bearing within said frame portion and engaged with said frame portion against axial movement relative thereto, whereby said step bearing transmits the downwardthrust of the shaft to said frame portion independently of said gear; land means engaged with said gear land extending to the exterior of said frame portion for rotating said gear to adjust said bearing vertically.

7. The structure defined in claim 6 in which the gear is a worm gear and the means is a worm.

References Cited in the file of this patent UNITED STATES PATENTS 652,208 Hadfield June 19, 1900 2,110,276 Rumpel Mar. 8, 1938 2,147,833 Fahrenwald Feb. 21, 1939 2,359,987 Gruender Oct. 10, 1939 2,448,936 Van Zandt Sept. 7, 1948 2,468,342 Munro Apr. 26, 1949 2,640,651 Gruender June 2, 1953 2,699,900 Traylor Jan. 18, 1955 

